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United States Patent |
5,119,886
|
Fletcher
,   et al.
|
June 9, 1992
|
Heat transfer cylinder
Abstract
A heat transfer method and apparatus are disclosed for transferring heat
across a cylinder surface, in order to maintain the cylinder surface at a
uniform temperature for drying, rolling or otherwise processing a work
piece. The apparatus comprises a rotatable cylinder wall with a plurality
of heat pipes bent near their evaporator ends and disposed within and
around the periphery of the cylinder wall, at least one end wall, and a
plurality of hubs interconnecting the cylinder with a drive shaft. The
heat transfer cylinder, itself, may comprise a large rotating heat pipe.
Inventors:
|
Fletcher; Leroy S. (College Station, TX);
Peterson, Jr.; George P. (College Station, TX)
|
Assignee:
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The Texas A&M University System (College Station, TX)
|
Appl. No.:
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426831 |
Filed:
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October 25, 1989 |
Current U.S. Class: |
165/89; 165/86; 165/104.25 |
Intern'l Class: |
F28D 015/02 |
Field of Search: |
165/86,89,47,104.25,90
|
References Cited
U.S. Patent Documents
3619539 | Nov., 1971 | Taylor | 165/89.
|
3801843 | Apr., 1974 | Corman et al. | 165/104.
|
3842596 | Oct., 1974 | Gray | 165/104.
|
3952798 | Apr., 1976 | Jacobson et al. | 165/89.
|
4064933 | Dec., 1977 | Schuman | 165/89.
|
4091264 | May., 1978 | Sarcia | 165/89.
|
4105896 | Aug., 1978 | Schuster | 165/89.
|
Foreign Patent Documents |
35388 | Mar., 1983 | JP | 165/86.
|
35389 | Mar., 1983 | JP | 165/86.
|
84086 | May., 1984 | JP | 165/86.
|
306321 | Jun., 1971 | SU | 165/104.
|
577386 | Oct., 1977 | SU | 165/104.
|
Primary Examiner: Davis, Jr.; Albert W.
Attorney, Agent or Firm: Arnold, White & Durkee
Claims
We claim:
1. A heat transfer cylinder for drying or otherwise processing a work
piece, said cylinder comprising: a cylinder rotatable about its
longitudinal axis and having an outer cylindrical wall surface; and a
plurality of heat pipes mounted within said cylinder and adapted to
transfer thermal energy to said outer cylindrical wall surface, each said
heat pipe comprising an evaporator portion and a condenser portion, said
evaporator portion of each said heat pipe extending sufficiently outward
relative to said longitudinal axis to increase the transfer of thermal
energy to said outer cylindrical wall surface during high speed rotation
of said cylinder.
2. A cylinder in accordance with claim 3, wherein said cylinder further
comprises an inner cylindrical wall surface, and wherein said condenser
portions of said heat pipes are disposed longitudinally within the
cylinder and essentially parallel to its longitudinal axis.
3. A cylinder in accordance with claim 2, wherein said heat pipes are
substantially evenly spaced around the periphery of said cylinder and
wherein said condenser portions within said cylinder are adjacent said
inner cylindrical wall surface.
4. An integrated heat pipe cylinder in accordance with claim 2, wherein
said condenser portions of said heat pipes within said cylinder are
integral with said cylinder, said condenser portions of said heat pipes
being disposed between said inner and outer cylinder surfaces.
5. A cylinder dryer for use in drying pulp or paper comprising: a cylinder
rotatable about its longitudinal axis and having an outer cylinder wall
surface adapted to contact said pulp or paper; and a plurality of heat
pipes mounted within said cylinder and adapted to transfer thermal energy
to said outer cylinder wall surface, each said heat pipe comprising an
evaporator portion extending outward relative to said longitudinal axis.
6. A cylinder roller for use in reducing the thickness of a work piece,
said cylinder roller comprising: a cylinder rotatable about its
longitudinal axis and having an outer cylinder wall surface adapted to
contact the work piece; a plurality of heat pipes mounted within said
cylinder and adapted to transfer thermal energy to said outer cylinder
wall surface, each said heat pipe comprising an evaporator portion
extending outward relative to said longitudinal axis.
7. A heat transfer cylinder for drying or otherwise processing a work
piece, said cylinder comprising: a cylinder rotatable about its
longitudinal axis and having an inner and an outer cylinder surface; a
plurality of heat pipes mounted within said cylinder, each said heat pipe
comprising an evaporator portion extending beyond one end of said cylinder
and outward relative to said longitudinal axis, and a condenser portion
within said cylinder; said condenser portions within said cylinder being
longitudinally disposed within said cylinder and around the periphery of
said cylinder; means for imparting thermal energy to said evaporator
portion of said heat pipes; and means for rotating said cylinder.
8. A heat transfer cylinder in accordance with claim 7, wherein said means
imparting thermal energy to said heat pipes comprises a source of steam.
9. A heat transfer cylinder in accordance with claim 7, wherein said means
for rotating said cylinder comprises at least one shaft rotatable about
its longitudinal axis and attached to said cylinder.
10. A heat transfer cylinder in accordance with claim 9, wherein said means
for rotating said cylinder further comprises a hub interconnecting said
one shaft and said cylinder.
11. A heat transfer cylinder for drying or otherwise processing a work
piece, said cylinder comprising: a cylinder rotatable about its
longitudinal axis and having inner and outer cylinder surfaces and first
and second ends; a plurality of closed heat pipes capable of holding a
vaporizable liquid, each said heat pipe comprising an evaporator portion
and a condenser portion capable of condensing vapor from the evaporator
portion, said evaporator portion extending beyond one end of said cylinder
and outward relative to said longitudinal axis, said evaporator portion
also being partially within said cylinder, and said condenser portion
being within said cylinder, said heat pipes being mounted in fixed
relation within said cylinder; means for imparting thermal energy to said
evaporator portion of said heat pipes; a first hub interconnecting said
first end of said cylinder with a rotatable drive shaft; and a second hub
interconnecting said second end of said cylinder with said drive shaft.
12. A heat transfer cylinder in accordance with claim 11, wherein said
second hub is open.
13. A heat transfer cylinder in accordance with claim 11, wherein said
first hub has a truncated conical shape having a larger diameter, closed
first end and a smaller diameter, open second end, said first hub defining
a hollow cavity such that said evaporator portions of said heat pipes
extend into said hollow cavity defined by said first hub.
14. A heat transfer cylinder in accordance with claim 13, wherein said
first hub partially houses said means imparting thermal energy to said
heat pipes.
15. A heat transfer cylinder in accordance with claim 14, wherein said
means imparting thermal energy to said heat pipes comprises a plurality of
steam input lines aimed at said evaporator portion of each said heat pipe,
and a plurality of condensate removal tubes having openings positioned
near the periphery of said first end of said first hub.
16. A heat transfer cylinder in accordance with claim 15, wherein said
steam input lines and said condensate removal tubes are cast inside said
first hub.
17. A heat transfer cylinder for drying or otherwise processing a work
piece, said cylinder comprising: a cylinder rotatable about its
longitudinal axis and having inner and outer cylinder wall surfaces and
first and second ends; an end wall enclosing said first end of said
cylinder; a plurality of heat pipes, each said heat pipe comprising an
evaporator portion and a condenser portion, the evaporator portion of each
said heat pipe extending through said first end of said cylinder, through
said end wall and outward relative to said longitudinal axis, said
condenser portions being longitudinally disposed and mounted within said
cylinder and around the periphery of said cylinder, said heat pipes being
adapted to transfer thermal energy to said outer cylinder wall surface.
18. A heat transfer cylinder for drying or otherwise processing a work
piece, said cylinder comprising:
a cylinder having at least an outer cylinder surface and first and second
ends;
a plurality of heat pipes disposed longitudinally the length of said
cylinder and mounted within and in a fixed relation to said cylinder, each
said heat pipe having first and second ends, each said heat pipe having an
evaporator portion and a condenser portion, and each said heat pipe being
bent at an angle and positioned so that the diameter formed by the
evaporator portions of said heat pipes is larger than the diameter formed
by the condenser portions of said heat pipes;
means for imparting thermal energy to said evaporator portion of each said
heat pipe, said means comprising a steam input line adapted for spraying
steam at said evaporator portion of each said heat pipe, and a plurality
of condensate removal tubes adapted for removing condensate; and
first and second hubs, said first hub interconnecting said cylinder with a
drive shaft, said second hub interconnecting said cylinder with another
shaft.
19. A heat transfer cylinder in accordance with claim 18, wherein said
evaporator portion of each heat pipe is at said first end of each heat
pipe, said evaporator portion of each heat pipe being positioned so that
it extends beyond said first end of said cylinder and into said first hub,
and wherein said means imparting thermal energy to said evaporator
portions of said heat pipes is partially contained in said first hub such
that said steam input lines spray steam on said evaporator portions of
said heat pipes within said first hub, and such that said condensate
removal tubes adapted for carrying away condensate are positioned inside
and near the periphery of said first hub.
20. A heat transfer cylinder in accordance with claim 19, wherein said
first hub is partially hollow, and wherein said first hub comprises a
closed first end and an open second end, said first end being mounted to
said drive shaft, and said open end being joined to said first end of said
cylinder to form a hollow cavity adjacent said first end of said cylinder,
said closed end of said first hub having a larger inside diameter than the
inside diameter of said open end of said first hub.
21. A heat transfer apparatus, comprising: a rotatable, cylindrical member
having an outer surface and a longitudinal axis; a plurality of heat
conducting pipes arranged within said cylindrical member essentially
parallel to said longitudinal axis thereof and adjacent said outer
surface, each said heat conducting pipe comprising an evaporator portion
extending beyond a first end of said cylindrical member and outward
relative to said longitudinal axis to enhance the transfer of thermal
energy during high speed rotation of said cylinder; a fluid sealed within
said heat conducting pipes, said fluid being capable of successively and
repeatedly vaporizing and condensing to transfer thermal energy along said
cylindrical member and to said outer surface; and means for heating said
evaporator portions of said heat conducting pipes in order to cause at
least a portion of said fluid to vaporize and to thereby transfer and
impart heat to said outer surface.
22. The apparatus as defined in claim 21, further including means for
causing said fluid, upon condensing, to travel to the heat portion of each
said heat conducting pipe.
23. The apparatus as defined in claims 21 and 22, further including a
chamber at said first end of said cylindrical member, and wherein said
evaporator portion of each said heat conducting pipe is at an end of each
heat conducting pipe and extends into said chamber.
24. A method of transferring heat to the outer wall surface of a
cylindrical member rotatable about its longitudinal axis, comprising the
steps of: providing a plurality of heat conducting pipes adjacent to and
interiorly of the outer wall surface of said cylindrical member; applying
heat to a portion of said pipes extending outward relative to said
longitudinal axis, and causing a fluid within said pipes to vaporize and
convey heat from said portion to other portions of the pipes and thereby
to the outer surface of said cylindrical member; whereupon the vaporized
fluid condenses for subsequent and repeated vaporization for heat
transfer.
25. The method defined in claim 24, further including the step of conveying
the condensed fluid back to that portion of the pipe where heat is
applied.
26. Apparatus for processing work pieces such as paper, paper pulp, metal
sheets and ingots, which comprises: a cylindrical member rotatable about
its longitudinal axis, said cylindrical member including first and second
ends and an outer wall surface adapted to receive and contact a work
piece; a plurality of heat pipes disposed along and within said
cylindrical member and distributed about the periphery of said cylindrical
member, each of said heat pipes including an evaporator portion proximate
said first end which extends longitudinally beyond said outer wall surface
and gradually outwardly along the length of said evaporator portion
relative to the longitudinal axis, and a condenser portion being generally
parallel to an disposed in heat transfer relation with said outer wall
surface; and a capillary structure disposed along and within said heat
pipe and extending between said evaporator and condenser portions.
27. The apparatus of claim 26 which further comprises a hub attached to
said first end of the cylindrical member and defining a cavity which also
houses said outwardly bending evaporator portions.
28. The apparatus of claim 26 which further comprises a first line
penetrating the hub along said longitudinal axis capable of supplying a
heating fluid into said cavity.
29. The apparatus of claim 28 which further comprises a second line
penetrating the hub along said longitudinal axis and capable of venting
said cavity, and a plurality of radially disposed conduits within said hub
communicating at their radially inner ends with said second line and at
their outer ends with the periphery of said cavity so as to vent said
cavity along said periphery.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
This invention relates generally to heat transfer apparatus, and more
specifically, to a rotating heated cylinder for producing or processing
materials or work pieces. Such cylinders may be used in a number of
industries including the pulp and paper industry, various metal rolling
industries, the food processing industry, the plastics industry, copy
machines, laminating machines, and many other applications. The invention
is of particular interest in the pulp and paper industry as a dryer and
the metal rolling industry as a roller.
2. Related Art
Multicylinder drying systems currently used in the pulp and paper industry
are composed of a series of cylinder dryers as schematically represented
in FIG. 1. Such drying systems may use up to about 70 cylinders, but a
typical newsprint or fine paper dryer system may use up to about 55
cylinders. The individual drying cylinders of these systems typically
comprise rotating pressure vessels that are heated by pressurized steam.
The use of pressurized steam as the heating medium for such dryers,
however, has several disadvantages. First, to be even minimally effective,
the steam in these cylinders must be heated to a temperature in excess of
350.degree. F. At 350.degree. F., the vapor pressure of steam is
approximately 135 p.s.i.a. Thus, these cylinders must be constructed to
meet pressure vessel codes and standards, making the manufacture of the
cylinders expensive and difficult.
Second, as the steam contained inside the cylinders condenses, varying
depths of condensate form on the cylinders' inner walls causing them to
have a nonuniformly heated outer surface. Similarly, condensate and excess
working fluid pools at the "bottom" of the cylinders as they rotate about
their horizontal axes. This also impedes uniform heating. These problems,
in turn, result in a nonuniform final product.
Third, the pressurized cylinders are inefficient and dangerous to operate.
For example, as described above, varying depths of condensate on the
inside of a cylinder cause nonuniform heating of the cylinder, and this
results in a nonuniform final product (e.g. the paper to be contact dried
in a pulp and paper mill is only partially dried). To correct this
problem, additional energy is typically added in an attempt to achieve a
uniform final product. This, of course, is inefficient. Likewise, the very
necessity of meeting steam pressure vessel codes and standards suggests an
element or possibility of danger associated with high pressure steam used
in these cylinders.
Another problem with prior art cylinders occurs in the aluminum, copper,
steel and other industries where metal sheets are rolled from ingots or
other feedstock into sheets (see FIG. 2). In these applications, the
inability of prior art cylindrical rollers to maintain a uniform roller
temperature during rolling of the metal causes an undesirable variation in
sheet thickness. As the ingots or other feedstocks are forced through
gradually smaller and smaller roll press openings, the surface areas of
the rollers coming in contact with the feedstocks heat up. At the ends of
the individual rollers, the heat is more easily dissipated than near the
middle of the rollers; therefore the rollers expand more around the
middle. The result is inefficient use of materials, poor quality control,
and variable strength characteristics in metal sheets having nonuniform
thickness (i.e., there is a region in the middle of the final metal sheets
where the metal is thinner than the outer sides of the sheets).
Various attempts have been made in prior art cylinders to alleviate some of
the problems described above. For example, H. L. Smith, Jr., U.S. Pat. No.
3,228,462, describes a cylinder dryer that uses a fluid heat transfer
medium, preferably liquid, which flows in opposite directions through two
independent, interested labyrinthine flow channels around the periphery of
the dryer cylinder. This working fluid is described preferably to be
liquid hydrocarbons which may be heated to temperatures of
500.degree.-800.degree. F. and higher without boiling or decomposing to a
significant extent. The patent further states that the heat transfer
medium is circulated in liquid form at low pressure, eliminating the
disadvantages attending high pressure steam and yet permitting higher
surface temperatures to be obtained than are practical in steam heated
drum dryers.
The cylinders described in the Smith reference, however, have various
problems associated with them. For example, most drying facilities are
already equipped with steam generating components. Therefore, to implement
the Smith dryers on a large scale in already existing factories would be
unduly expensive. Furthermore, manufacturing the internested labyrinthine
flow channels disclosed in Smith, to achieve even a substantially
uniformly heated cylinder, would be highly exacting, expensive and
difficult. This is not to mention the expense and difficulty associated
with manufacturing such channels and cylinders so that they do not leak
the working fluid to undesired locations.
Hemsath, et al., U.S. Pat. No. 4,693,015, uses a direct firing burner which
oxidizes fuel and directs hot combustion gases into the center of a dryer.
The gases are then recirculated to nozzle assemblies contained in a
plurality of extending boxes positioned around the periphery of the dryer
cylinder. This system of direct firing of a flammable gas into each
individual cylinder is inefficient, expensive and dangerous to operate.
Moreover, most pulp and paper factories are equipped with steam heating
components, and it would be expensive to replace them all with direct
firing burners. Likewise, direct oxidation of a flammable fuel at up to 70
or more dryer cylinder locations, with the attendant possibility of fuel
leaks and explosions, can be highly dangerous.
Schuster, U.S. Pat. No. 4,105,896, describes a double-walled hollow
cylinder which is heated by an evaporation and condensation chamber formed
between the inner and outer walls of the cylinder. This patent further
states that the evaporation and condensation chamber has a larger outside
diameter at either end of the cylinder than the outside diameter of the
rest of the cylinder in between. The larger outside diameter, together
with the inner cylinder wall, defines annular compartments or vapor
generators at both ends of the cylinder. These annular compartments have
steel wool packing in them to enhance vaporization. Upon heating a liquid
working fluid contained in these annular compartments with an electrical
slip ring/brush combination, the working fluid vapors travel from the
annular compartments into the hollow cylindrical chamber defined by the
inner and outer cylinder walls, thereby heating the cylinder surface that
contacts a work piece.
Unfortunately, Schuster does not solve the problem of varying depths of
condensate on the inner cylinder wall causing nonuniform heating of the
working surface of the cylinder. Also, the problem of meeting pressure
vessel requirements is only partly overcome to the extent that Schuster
describes use of a carbon fluoride working fluid having a lower vapor
pressure than other kinds of working fluids.
A heat pipe roller used in laminating and copy machines is described in
Sarcia, U.S. Pat. No. 4,091,264, and Jacobson et al., U.S. Pat. No.
3,952,798. The heat pipe roller disclosed by these patents uses an
internal, axially positioned, heat source and makes use of a wicking
structure that extends radially from the heat source to cover the
cylinder's inner surface. Likewise, the heat pipe roller of Sarcia and
Jacobson contains a working fluid which is partially absorbed into the
wicking structure and brought towards the heat source by capillary action,
gravity and a paddle wheel-like action resulting from rotating the roller
having radially extending wicking components inside.
The foregoing prior art rollers make no attempt to solve the need for
costly and difficult pressure vessel construction. Also, such rollers are
not suitable for high speed rotation necessary in many roller and cylinder
dryer applications. This is because the working fluid of these rollers
will be forced out away from the axial heat source as the roller rotates
at higher and higher revolutions per minute (rpm's), and thus the working
fluid will not be adequately vaporized. Such rollers are therefore limited
to slow rotating applications. Also, the references describing these
rollers show no awareness of the problems inherent in vaporizing a working
fluid inside the roller itself (i.e., varying levels of condensate causing
nonuniform heating, and the adverse effects on temperature uniformity of
working fluid pooling at the "bottom" of the roller).
Heat pipes per se are well known. Generally, a heat pipe comprises a sealed
tube containing a working fluid and a capillary structure. In choosing a
suitable working fluid, one skilled in the art will consider the physical
properties of the fluid and the desired characteristics of the heat
transfer cylinder. "[T]he choice of a working fluid is dependent on
physical properties of the fluid and compatibility of the fluid with the
wicking structure. Among properties which will be considered by one
skilled in the art are: vapor pressure, thermal conductivity, viscosity,
and density of vapor and liquid" (see Sarcia, U.S. Pat. No. 4,091,264
citing Articles and U.S. Patents).
The capillary structure in a heat pipe may be made of any suitable material
providing capillary attraction to a particular working fluid. For example,
grooves etched into the heat pipe, wire lattices, and wicking material
have all been used as capillary structures in heat pipes. Energy transfer
within a heat pipe is basically accomplished in a cycle. To start the
cycle, heat is applied to one end of the pipe (the evaporator part),
thereby raising the temperature of the working fluid inside the pipe above
its vaporization temperature. As the vapor leaves the evaporator portion
of the heat pipe, it fills the rest of the pipe where the temperature is
slightly lower than the evaporator part. This causes the vapor, now evenly
distributed throughout the heat pipe to condense, thereby releasing
additional thermal energy. To complete the cycle, the condensate is drawn
back towards the evaporator through the above described capillary
structure within the pipe.
SUMMARY OF THE INVENTION
The present invention overcomes many of the prior art problems through the
use of a plurality of heat pipes in a heat transfer cylinder, in
accordance with one aspect of the invention. Such a heat transfer cylinder
is suitable for use in several situations including, but not limited to,
the following: the pulp and paper industry, the metal rolling industry,
the food processing industry, the plastics industry, copy machines,
laminating machines etc.
As shown below, heat pipes are uniquely suited to transfer thermal energy
uniformly across a rotating cylindrical surface for drying, rolling or
otherwise processing a work piece. Thermal energy transfer within the
individual heat pipes of the present invention occurs in a very efficient
cycle. This cycle is begun by applying heat to a portion of the heat pipe.
The portion of each heat pipe where heat is applied, is known as the
evaporator portion of the heat pipe. In the first embodiment of the
invention, that portion is preferably at the end of the heat pipe;
however, it will be appreciated that the heat pipe may be heated at any
location without departing from the scope of the invention.
As the working fluid within the evaporator portion of each heat pipe is
raised above its vaporization temperature, vapor leaves the evaporator
portion of each heat pipe and fills the rest of the pipe. Upon reaching
the area of the pipe having a slightly lower temperature than the
evaporator portion of the heat pipe--i.e., the condenser portion of the
heat pipe--the vapor condenses, giving off thermal energy which is
conducted to adjacent structures such as the outer cylinder surface.
To complete the cycle of thermal energy transfer within each heat pipe, the
condensate is absorbed into the capillary structure within the heat pipe.
This capillary structure may be made of any suitable material providing
capillary attraction to a particular working fluid. For example, grooves
etched into the heat pipe, wire lattices, and wicking material have all
been used for this capillary structure.
The heat transfer cylinder of the first embodiment of the invention
comprises a cylinder wall having first and second ends and inner and outer
surfaces, or at least an outer surface in the case of a solid cylinder,
and at least one end wall. These elements are preferably made of cast
metal, but such material is not absolutely necessary. The cylinder wall of
the heat transfer cylinder is adapted to carry a plurality of heat pipes
which, upon continuous completion of the above described cycle, transfer
thermal 15 energy uniformly to the outer surface of the cylinder wall
which comes in contact with a work piece. To best accomplish uniform
heating of the cylinder's outer surface, these heat pipes are preferably
disposed longitudinally the length of the cylinder wall, and are
preferably distributed frequently and evenly around the cylinder wall's
circumference. The heat pipes may be mounted adjacent the inside surface
of the cylinder wall or may be made integral with the cylinder wall as by
investment casting, rotary casting with heat pipe cores, or insertion of
heat pipes into preformed receptacles.
While a preferred position of the heat pipes in the present invention is
longitudinally disposed and adjacent the inner surface of the cylinder
wall, or integral with the cylinder wall, it will be appreciated by those
skilled in the art that other heat pipe configurations relative to the
cylinder wall will be possible without departing from the scope of the
invention.
A preferred embodiment of the invention further provides that the cylinder
wall is engaged at its first and second ends by a hub: namely a steam
chest hub rigidly joined to the first end of the cylinder wall and an open
hub rigidly joined to the second end of the cylinder wall.
The steam chest hub, in a preferred embodiment of the invention, is in the
shape of a hollow truncated cone with a large closed end and a smaller
open end. This steam chest 10 hub is mounted at its open end to the first
end of the cylinder wall, and adjacent the evaporator portions of the heat
pipes. Thus, the evaporator portions of the heat pipes extend beyond the
first end of the cylinder wall, through the end wall enclosing the first
end of the cylinder wall, 15 and into the enclosed cavity formed by the
steam chest hub and the end wall. The steam chest hub is joined to the
cylinder wall by welding or other suitable means to the first end of the
cylinder sealing the cavity formed between the first end wall and the
steam chest hub. At its closed end, the steam chest hub is rigidly mounted
to a drive shaft. Thus, the steam chest hub interconnects the cylinder
wall with the drive shaft which rotates the cylinder about its axis during
operation.
In another aspect of a preferred embodiment of the invention, the drive
shaft does not extend through the cylinder, but instead ends at or inside
the steam chest hub. Another shaft is rigidly connected at one end to the
open hub rigidly joined to the second end of the cylinder wall. At its
other end, this other shaft is mounted on a bearing fixture allowing
rotation of the shaft. Therefore, this other shaft works together with the
drive shaft allowing the heat transfer cylinder to rotate about its axis.
Of course, it will be apparent to those skilled in the art that a single
drive shaft keyed or otherwise rigidly attached to the hubs and extending
through the area defined by the cylinder wall can be used. Likewise, any
well known motor and drive system may be employed to rotate the drive
shaft and thereby rotate the heat transfer cylinder which is, in effect,
an integrated heat pipe cylinder or roller.
Further, the steam chest hub is adapted to receive a steam input line from
the drive shaft. Once the steam input line enters the steam chest hub from
the drive shaft, it branches radially into a plurality of steam input
lines (or passageways) ending in nozzles, with preferably one steam input
line corresponding to each heat pipe. These steam input lines are disposed
within the steam chest hub with their nozzles adjacent the evaporator
portion of each heat pipe to spray hot steam thereon during operation of
the cylinder.
Likewise, the steam chest hub is adapted to house condensate removal tubes
(or passageways) with openings inside the steam chest hub. These tubes
carry condensate forming within the steam chest hub to the steam
generator. To accomplish this, the condensate removal tubes branch
radially from an inner concentric shaft entering the steam chest hub
through the outer drive shaft, the openings of the tubes being positioned
inside and near the periphery of the steam chest hub where condensate
collects by centrifugal forces during rotation of the hub. To drain the
condensate, a vacuum is created in the condensate removal tubes which
sucks the condensate out of the steam chest hub and carries it to a steam
generator.
To enhance condensate removal from the steam chest hub, the hub is
preferably in the form of a hollow truncated cone as described above
having open and closed ends. Thus, upon rotation of the cylinder wall and
hub, condensate within the hub is forced by centrifugal force to collect
near the closed end of the steam chest hub (i.e., the end where the
diameter of the steam chest hub is greater than the open end of the hub
sealed to the first end of the cylinder wall).
The use of steam through the steam chest hub is only one preferred way,
among many other well known ways, of 10 heating the evaporator portions of
the heat pipes. For example, an electrical slip ring/brush combination,
direct fire combustion, hot gases, or other well known methods of heating
may be suitably used in the present invention without departing from its
scope. Likewise, those skilled in the art will note that it is not
necessary to heat the ends of the individual heat pipes or cylinder wall
with an external heat source; instead, the pipes or cylinder wall may be
heated internally and/or at varying locations along the pipes with varying
degrees of efficiency.
At the second end of the cylinder opposite the end rigidly joined to the
steam chest hub, the cylinder wall is rigidly joined to an open hub, e.g.,
a hub containing holes in it. The open hub is suitable since it is not
necessary to enclose the second end of the cylinder wall in this
embodiment of the invention because the working fluid used in this
embodiment of the invention is contained within the individual heat pipes
of the cylinder. However, though an open hub is preferable because it uses
less material and weighs less, a solid hub may be used. The center of the
open hub is rigidly connected to a shaft that is mounted on bearings to
allow rotation of the heat transfer cylinder.
While several additional hubs may be disposed throughout the cylinder for
various purposes well known to those skilled in the art, a preferred
embodiment of the invention only uses two hubs as above described.
During operation of the thermal transfer cylinder, thermal energy is
uniformly transferred across the outer surface of the cylinder wall.
Basically, operation of the cylinder consists of rotating the cylinder
about its axis, heating the evaporator portions of the heat pipes disposed
within the cylinder, and removing steam condensate from the steam chest
hub. As the heat pipes undergo heating at their evaporator portions, they
commence the thermal energy transfer cycle above described, imparting heat
typically by conduction and/or thermal radiation to surrounding
structures, most importantly to the adjacent outer cylinder 15 surface
coming in contact with the work piece. As noted earlier, the work piece
can be paper in a paper dryer assembly, a composite laminate in a
laminating machine, a rolled piece of dough in a dough rolling machine, an
ingot of steel, aluminum or copper in a metal rolling mill or a piece of
paper in a copy machine.
In another aspect of the invention, the heat pipes are bent slightly
outwardly so that the diameter formed by the evaporator portions of the
heat pipes is slightly larger than the diameter formed by the condenser
portions of the heat pipes. This aspect of the invention enhances the
transfer of thermal energy in the individual heat pipes as the cylinder
containing the heat pipes is rotated at higher rpm's thereby improving the
efficiency of the cylinder.
For example, currently in the pulp and paper industry, many cylinder dryers
operate at approximately 200-300 rpm's with six foot cylinder diameters.
However, those skilled in the pulp and paper industry desire to operate
between 300-500 rpm's and possibly higher with up to eight foot diameter
cylinders. The present invention is particularly suited to achieve such
results because the desired larger diameter cylinder surfaces can easily
be uniformly heated by using more heat pipes in the cylinder. Furthermore,
the higher the rotational velocity of the cylinder, the more efficiently
the cylinder surface is heated because of the outwardly bent pipes
described above. In other words, the higher the rotational velocities in
the particular application, the more efficient is the cylinder of the
present invention at transferring thermal energy across the cylinder's
outer surface. On the other hand however, this advantageous characteristic
of the invention at high rpm's does not adversely affect the improved
efficiency of the invention over prior art cylinders at very low rpm's.
Heat pipes are particularly suited to the transfer of heat across a
cylindrical rolling or drying surface because of high efficiency in
providing thermal energy transport across the surface of the cylinder, and
the heat pipe's ability to quickly dissipate localized concentrations of
heat from any area of the cylinder surface. The velocity of the vapor
within the individual heat pipes is very fast, having been measured
approaching Mach one. Also, the heat transfer process described above is
driven by a very minimal temperature gradient between the evaporator
portions and the condenser portions of the heat pipes. Indeed, it is a
well known characteristic that the transfer of large quantities of energy
in heat pipes, being an isothermal transfer process, can be accomplished
at a wide range of temperatures, both high and low. Furthermore, heat
pipes can easily be made to the precise length of the outer cylinder
surface contacting the work piece so that heat is evenly distributed
longitudinally the length of the surface. Likewise, the size and number of
heat pipes can be varied so that circumferential uniformity is achieved
and maintained constant.
The present invention allows the surface temperature of the cylinder to be
maintained uniformly at the desired temperature. This is achieved by
directly and simultaneously applying the same temperature heat source
(e.g., steam, direct firing oxidation, electricity, etc.), to all the
evaporator portions of the heat pipes. Thus, to being, there is virtually
no temperature loss or difference between the evaporator portions of the
heat pipes. This initial temperature uniformity at the evaporator portions
of the heat pipes is maintained as thermal energy is transferred along the
heat pipes, for it is a well known and measured characteristic of heat
pipes to quickly, consistently and uniformly conduct thermal energy along
their length with virtually no temperature drop. Thus, the temperature
along the heat pipes, and hence along the cylinder surface, is uniform. In
regard to maintaining temperature uniformity, it is also a well known
characteristic of heat pipes of dissipate heat from sources other than the
desired heat source (e.g., heat from friction between the work piece and
the cylinder). Hence, the cylinder is not only efficiently and uniformly
heated by the heat pipes, but it is also maintained at a uniform
temperature during operation of the cylinder despite heat input to the
cylinder from other sources.
All of these considerations make the heat pipe particularly suited to
maintain a uniformly heated cylinder surface under the various conditions
in which such cylinders are used. The heat transfer cylinder of the
invention thereby addresses the problems left unsolved by prior art
cylinders. For example, the invention helps to eliminate condensate on the
cylinder wall's inner surface, and thus alleviates the problem of
nonuniform heating attributed to varying depths of condensate on the
cylinder wall's inner surface. Likewise, the present invention is more
efficient because there is no longer the need for extra heating of the
cylinder in an attempt to compensate for nonuniform temperatures due to
varying depths of condensate inside the cylinder.
Furthermore, the need for pressure vessel construction of the cylinder is
no longer necessary because only the heat pipes contain pressurized vapor,
not the cylinder itself. This, in turn, reduces the expense of producing
such cylinders because less material is needed and stringent pressure
vessel codes need not apply. Since the cylinder walls themselves are not
subject to vapor pressure, maintenance is easier and less frequent and
operation of the cylinder is therefore safer than prior art cylinders.
An alternative embodiment of the invention comprises the application of the
heat pipe principle to a rotating cylinder for drying, rolling or
otherwise producing or processing a work piece. As with the first
embodiment of the invention described above, this embodiment of the
invention comprises an end wall enclosing the first end of the cylinder
wall and two hubs, a steam chest hub and a closed hub. Likewise, the
methods of heating and rotating this second embodiment of the invention
are substantially identical to those in the first embodiment of the
invention.
The steam chest hub used with the second embodiment of the invention is
virtually identical to the steam chest hub in the first embodiment of the
invention, serves substantially the same purposes, and is joined to the
cylinder wall and drive shaft in basically the same way. Likewise, this
embodiment of the invention also comprises virtually identical steam input
lines and condensate removal tubes. These components function in the same
way, and are positioned similarly to corresponding components in the first
embodiment of the invention. However, the steam input lines of the second
embodiment of the invention are preferably slightly longer and positioned
differently than their counterparts in the first embodiment. This allows
direct spraying of steam onto the first end of the cylinder wall itself as
required in the second embodiment.
Further, in the second embodiment of the invention, the hub joined to the
second end of the cylinder wall is a closed hub. Unlike the corresponding
open hub in the first embodiment, this closed hub does not have holes in
it because it must enclose and seal the hollow cylinder formed by the
cylinder wall and the end wall. As with the open hub of the first
embodiment, the closed hub of the second embodiment is also rigidly
mounted on a shaft other than the drive shaft. In this manner, the closed
hub interconnects the heat transfer cylinder with the other shaft.
It will be recognized that either single or dual shafts may be used to
rotate the second embodiment of the invention and that more than two hubs
may be used. Likewise, as described above, it will be understood that the
second embodiment of the invention is also suitably heated by other well
known heat sources such as electricity, direct fire oxidation and others.
Furthermore, it is apparent that the second embodiment of the invention
may be used in all of the same situations as the first embodiment.
Inasmuch as thermal energy is applied to the first end of the cylinder wall
in the second embodiment of the invention, this first end of the cylinder
wall becomes the evaporator portion of the cylinder, and the rest of the
cylinder wall is the condenser portion of the cylinder. Though applying
heat to the end of the cylinder wall, as described above, is preferred,
those skilled in the art will see that the heat source may be directed at
any portion of the cylinder wall, making that portion the evaporator
portion and the rest of the cylinder wall the condenser portion.
Unlike the first embodiment of the invention where individual heat pipes
contain the capillary structure and the working fluid, the inside surface
of the cylinder wall of the second embodiment is preferably lined with a
capillary structure (e.g., grooves, wires, wicking material or other
material serving a capillary function), and the cylinder itself is adapted
to receive and contain the working fluid.
During operation of the second embodiment of the invention, heat is applied
to the evaporator portion of the rotating cylinder itself in much the same
way as heat is applied to evaporator portions of the heat pipes of the
first embodiment. This causes the working fluid sealed inside the cylinder
wall, end wall and closed hub to vaporize and fill the rest of the
cylinder. After leaving the evaporator portion of the cylinder, the vapor
gradually cools and condenses. The heat given off during condensation is
transferred by conduction to the outer surface of the cylinder. The
condensate is then reabsorbed into the capillary structure etched or
otherwise provided on the inner surface of the cylinder, and is brought
back towards the evaporator portion of the cylinder through capillary
and/or centrifugal forces.
In accordance with another aspect of this second embodiment, the evaporator
portion of the cylinder is flared outwardly so that the diameter of the
evaporator end of the cylinder is slightly larger than the diameter of the
rest of the cylinder. In this manner, additional acceleration forces are
added which, in addition to otherwise existing centrifugal and/or
capillary forces, move condensate more rapidly away from the condenser
portion of the cylinder and towards the evaporator portion of the
cylinder. These forces enhance the transfer of thermal energy across the
cylinder and become greater as the cylinder is rotated at higher and
higher speeds. This is especially significant, as described above, since
some applications require that the heat transfer cylinder of the present
invention operate at very high rotational velocities. Indeed, the flared
structure of the present embodiment, used in conjunction with the inner
capillary structure regulating the working fluid depth on the cylinder
walls, greatly enhances the efficiency of the present invention over prior
art cylinders.
As described above, heat pipes are particularly suitable for rotating
cylinders for drying, rolling or otherwise processing a work piece. This
is also true with the second embodiment of the invention. The heat
transfer cylinder of the second embodiment of the invention achieves a
high degree of conductance, heat dissipation, and constant uniform heating
across the cylinder's outer surface. In addition, the advantageous
properties of high speed vapor travel and isothermal energy transfer exist
in the second embodiment of the invention. Indeed, the various
characteristics described above demonstrate the applicability of general
heat pipe principles to cylinders used for drying, rolling, or otherwise
processing a work piece.
The second embodiment of the present invention addresses many of the
problems left unsolved by prior art cylinders. For example, the addition
of a capillary structure into the cylinder, especially when the cylinder
rotates at high speeds, serves to control the depth of working
fluid/condensate on the inside surface of the cylinder wall. Likewise,
unlike conventional steam cylinder dryers and rollers, only a relatively
small, predetermined amount of liquid is present inside the cylinder. This
is due to the fact that the cylinder is sealed once the working fluid is
introduced, with the heat source being external to the cylinder walls. To
the contrary, conventional steam cylinders spray steam directly into the
cylinder so that condensate pools at the "bottom" of the cylinder and
exists at varying depths on the cylinder's inner surface. These
considerations demonstrate the ability of the second embodiment of the
present invention to achieve a more efficiently and uniformly heated outer
cylinder surface. Likewise, the flaring of the evaporator portion of the
cylinder improves the transfer of thermal energy across the cylinder
surface, and makes the heat transfer cylinder of the present invention
more efficient than prior art cylinders.
Just like the first embodiment of the invention, the second embodiment of
the invention can be advantageously used in many applications including:
the pulp and paper industry, various metal rolling industries, the food
processing industry, the plastics industry, copy machines, laminating
machines, and others. Applied in such areas of commerce, the second
embodiment of the invention will greatly enhance efficiency, quality of
produces and profitability.
The subject matter of the present invention is particularly pointed out and
distinctly claimed in the concluding portion of this specification.
However, both the organization and method of operation of the invention,
together with further advantages thereof, may best be understood by
reference to the following description taken in connection with the
accompanying figures wherein like reference characters refer to like
elements.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a partial schematic representation of a typical drying system in
the pulp and paper industry;
FIG. 2 is a partial schematic representation of a metal rolling mill;
FIG. 3 is a longitudinal cross-section view of an individual heat pipe of
the first embodiment of the present invention;
FIG. 4 is a side view elevation of a heat transfer cylinder in accordance
with the first embodiment of the present invention;
FIG. 5 is a longitudinal cross-section view of the heat transfer cylinder
of FIG. 4 taken at line A--A;
FIG. 6 is an end view of the open cylinder hub of the heat transfer
cylinder of FIG. 4;
FIG. 7 is a cross-section view of the steam chest hub, the drive shaft, the
inner concentric shaft, the steam input lines and the condensate removal
tubes of FIG. 4 taken at line E--E;
FIG. 8 is a cross-section view of the heat transfer cylinder of FIG. 4
taken at line B--B;
FIG. 9 is a side view elevation of a heat transfer cylinder in accordance
with a second embodiment of the invention;
FIG. 10 is a longitudinal cross-section view of the heat transfer cylinder
of FIG. 9 along line C--C;
FIG. 11 is an end view of the solid hub of the heat transfer cylinder of
FIG. 9;
FIG. 12 is an end view of the steam chest hub of the heat transfer cylinder
of FIG. 9; and
FIG. 13 is a cross-section view of the heat transfer cylinder of FIG. 9
taken along line D--D.
DETAILED DESCRIPTION OF THE DRAWINGS
Referring to FIGS. 3-8 of the drawings, a heat transfer cylinder in
accordance with a first embodiment of the present invention is shown. The
first embodiment of the invention uses a plurality of heat pipes 10 in the
heat transfer cylinder 12 for drying, rolling or otherwise processing a
work piece. As described in further detail below, such heat pipes are
uniquely suited to heat transfer cylinders as used in various applications
including, but not limited to, the following: the pulp and paper industry,
various metal rolling industries, the food processing industry, the
plastics industry, copy machines, laminating machines, and many others.
Depending on the application involved, one or many heat transfer cylinders
12 may be used in a system to accomplish a desired result (e.g., drying
paper or flattening feedstock as illustrated in FIGS. 1 and 2). For
example, FIG. 1 schematically illustrates part of a cylinder dryer system
typical in a pulp and paper mill. Such a system generally comprises:
cylinder dryers 3, felt dryer cylinders 4, felt rolls 5, paper 6, felt 7,
felt guides 8 and felt stretchers 9, all working together in a system for
drying paper as shown. The present invention would be of use in any of the
dryers in such a system. For another example, FIG. 2 schematically
illustrates part of a roller assembly in a metal rolling mill where
cylinder rollers 11 are mounted on frame 15 so that they can rotate about
their axes to reduce the thickness of feedstock 13 (e.g. steel, aluminum
or copper). The present invention would also apply to such cylinder
rollers 11.
Referring again to FIGS. 3-8, a heat pipe 10, one of the plurality of heat
pipes used in heat transfer cylinder 12, is shown. Heat pipe 10 preferably
comprises an elongated tube 14 having first and second ends 16 and 18
sealed by end caps 17 and 19. Elongated tube 14 of heat pipe 10 also
contains a working fluid/condensate 20 absorbed in a capillary structure
22 (e.g., grooves, wires, wicking material or the like).
In one embodiment of the invention, heat is preferably applied to the first
end 16 of heat pipe 10, raising working fluid/condensate 20 to its
vaporization temperature. Thus, in this first embodiment of the invention,
the first end 16 of the heat pipe 10 is the evaporator portion 24 of the
heat pipe, and the rest of the heat pipe is the condenser portion 26.
Nonetheless, it will be apparent to those skilled in the art that heat
pipes 10, as used in the present invention, may be heated at differing
areas without departing from the scope of the invention.
Upon raising the working fluid/condensate 20 above its vaporization
temperature, vapor 28 leaves the evaporator portion 24 of the heat pipe 10
and fills the entire heat pipe. Upon reaching the condenser portion 26 of
the heat pipe 10, the vapor 28 condenses giving off thermal energy.
Turning specifically to FIGS. 4-8, heat transfer cylinder 12 comprises a
cylinder wall 30 with first and second ends 32, 34 and inner and outer
surfaces 36, 38. Heat transfer cylinder 12 further comprises at least one
circular end wall 40 that is joined to the cylinder wall 30, and which
encloses the cylinder adjacent the first end of the cylinder wall. Lining
the inner surface 36 of the cylinder wall 30 is insulation 39, which
serves to reduce heat loss into a hollow space 41 formed by the cylinder
wall and end wall 40. While a preferred embodiment of the invention
comprises a hollow cylinder (i.e., the cylinder wall 30 having inner and
outer surfaces 36, 38), it will be apparent to those skilled in the art
that a solid cylinder may be used in the present invention.
In accordance with the first embodiment of the invention, the heat pipes 10
of heat transfer cylinder 12 are preferably disposed longitudinally the
length of the cylinder wall 30, and are distributed substantially evenly
around the periphery of the cylinder wall. These heat pipes 10 may be
mounted adjacent t he inner surface 36 of the cylinder wall 30 or may be
made integral with the cylinder wall as by investment casting, rotary
casting with heat pipe cores, or insertion of heat pipes into preformed
receptacles.
While a preferred position of the heat pipes 10 in the present invention is
longitudinally adjacent or integral with the inner surface 36 of the
cylinder wall 30, it will be appreciated by those skilled in the art that
other heat pipe configurations relative to the cylinder wall will be
possible without departing from the scope of the invention.
The first embodiment of the heat transfer cylinder 12 of the invention
further comprises cylinder wall 30 being rigidly joined at its first end
32 to a steam chest hub 42, while the second end 34 of the cylinder wall
is rigidly joined to an open hub 43.
The steam chest hub 42, in a preferred embodiment of the invention, is
shaped like a hollow truncated cone or a bell with a large closed end 44
and a smaller open end 46. Steam chest hub 42 is rigidly joined at its
open end 46 to the first end 32 of the cylinder wall 30 adjacent the
evaporator portions 24 of the heat pipes 10. Thus, the evaporator portions
24 of the heat pipes 10 extend beyond the first end 32 of the cylinder
wall 30, through the end wall 40 enclosing the first end of the cylinder
wall, and into the enclosed cavity 48 formed by the steam chest hub 42 and
the end wall 40. The steam chest hub 42 is joined by welding or other
suitable means to the first end 32 of the cylinder wall 30, sealing the
cavity 48 formed between the end wall 40 and the steam chest hub 42. At
its closed end 44, the steam chest hub 42 is rigidly mounted to a hollow
drive shaft 50 supported by bearings 52 and extending from a motor or
other driving device (not shown).
Thus, the steam chest hub 42 interconnects the cylinder wall 30 with the
drive shaft 50. In this manner, the drive shaft 50 rotates the cylinder
wall 30, the heat pipes 10 mounted to or integral with the cylinder wall,
the end wall 40, the steam chest hub 42 and the open hub 43, about the
drive shaft axis during operation of heat transfer cylinder 12. Positive
rotation of the heat transfer cylinder 12 about drive shaft 50 is attained
by well known methods, such as keying the drive shaft to the hubs 42, 43
or otherwise.
In the first embodiment of the invention, drive shaft 50 ends at or just
inside the steam chest hub 42. Also, as further shown in FIG. 7, drive
shaft 50 is preferably hollow, having an inner concentric shaft 54
disposed longitudinally within and interconnected to the drive shaft by
fins 56. Another shaft 58, having first and second ends 60, 62, is rigidly
connected, at its first end 60, to the open hub 43, the open hub being
rigidly joined to the second end 34 of the cylinder wall 30. This other
shaft 58 is mounted at its second end 62 to a fixture with bearings 64 so
that heat transfer cylinder 12, being driven by drive shaft 50, is free to
rotate about its axis. Thus, shaft 58 works together with the drive shaft
50 to rotate the heat transfer cylinder 12 about its axis and the axes of
the shafts.
Despite the use of a plurality of shafts in the first embodiment of the
invention, it will be apparent to those skilled in the art that a single
drive shaft (not shown), extending along the longitudinal axis of the heat
transfer cylinder 12, may be used to rotate the heat transfer cylinder
about its longitudinal axis without departing from the scope of the
invention.
Steam chest hub 42 is further adapted to receive a steam input line 66,
being the annular space formed between inner concentric shaft 54 and the
drive shaft 50. Once the steam input line 66 enters the steam chest hub 42
through the drive shaft 50, it branches radially into a plurality of steam
input lines 68 ending in nozzles 70, preferably with one steam input line
68 corresponding to each heat pipe 10. These radially branching steam
input lines 68 are disposed within the steam chest hub 42 with their
nozzles 70 adjacent the evaporator portion 24 of each heat pipe 10 to
spray steam thereon.
Likewise, the steam chest hub 42 is adapted to house condensate removal
tubes 72 having openings 74. Within the steam chest hub 42, these
condensate removal tubes 72 branch radially from the inner concentric
shaft 54 so that the openings 74 of the condensate removal tubes 72 are
located near the periphery of the steam chest hub and adjacent its closed
end 44. So positioned, the openings 74 of these condensate removal tubes
72 can receive pooled condensate 76, the condensate having been forced
radially outwardly and towards closed end 44 of the steam chest hub 42 by
centrifugal force. Thereupon, condensate removal tubes 72 carry condensate
76 towards inner concentric shaft 54 which then carries the condensate to
an external steam generator (not shown). To perform this draining of the
condensate 76, a vacuum is created in the inner concentric shaft 54 and
the condensate removal tubes 72, the vacuum serving to suck the condensate
from steam chest hub 42 through the condensate removal tubes and into the
inner concentric shaft.
The above described truncated cone shaped design of the steam chest hub 42
enhances removal of condensate 76 from the steam chest hub. This is
because the diameter at closed end 44 of steam chest hub 42, near which
the openings 74 of condensate removal tubes 72 are located, is greater
than the diameter of the steam chest hub at open end 46 joined to cylinder
wall 30. Thus, upon rotation of the cylinder 12 (including rotation of
steam chest hub 42), condensate 76 within steam chest hub 42 is
centrifugally forced to collect near the closed end 44 of the steam chest
hub.
Those skilled in the art will realize that the use of steam input lines 68
and condensate removal tubes 72 is only one method of transferring steam
to heat pipes 10 and condensate from the steam chest hub. For example,
passageways (not shown) serving the same purpose may be cast into the
steam chest hub itself. Also, while several additional hubs (not shown)
may be disposed throughout the cylinder formed by the cylinder wall 30,
for various purposes well known to those skilled in the art, a preferred
embodiment of the invention only uses the two hubs 42, 43 as above
described. Likewise, the use of steam through the steam chest hub 42 is
only one preferred way, among many other well known ways, of heating the
evaporator portions 24 of the heat pipes 10. For example, an electrical
slip ring/brush combination with electric heaters, direct fire combustion,
hot gases, or other well known methods of heating may be suitably used in
the present invention without departing from its scope. Furthermore, those
skilled in the art will note that it is not necessary that the heat pipes
10 be heated at their first ends 16 and in the same manner as described
and shown above. Instead, those skilled in the art will appreciate that
the scope of the invention allows that the heat pipes may be heated by
either an external or internal heat source and/or at varying locations
along the heat pipes.
At the second end 34 of the cylinder wall 30, opposite the first end 32
joined to the steam chest hub 42, the cylinder wall is rigidly joined to
an open hub 43, for example, a hub containing holes in it. Open hub 43 is
suitable for the present invention because it is not necessary to enclose
the cylinder wall 30 in this embodiment of the invention; the working
fluid used in this embodiment of the invention is contained within the
individual heat pipes 10 of the heat transfer cylinder 12. However, though
an open hub 43 is preferable because it uses less material and weighs
less, a solid hub without any holes may be used. At its center, the open
hub 43 is rigidly connected to shaft 58 that is mounted on bearings 64 to
allow rotation of the heat transfer cylinder 12. In view of the rigid
connections between the drive shaft 50, the steam chest hub 42, the
cylinder wall 30, the open hub 43, and the other shaft 58, it is apparent
that these elements, together with the steam input lines 68 and condensate
removal tubes 72, rotate as a whole, in fixed relation to one another.
During rotation of the cylinder 12, steam is applied to the evaporator
portion 24 of heat pipes 10 which heats working fluid/condensate 20
located in the evaporator 15 portions of the heat pipes. Upon raising the
working fluid/condensate 20 above its vaporization temperature, vapor 28
leaves the evaporator portions 24 of the heat pipes 10 and fills the heat
pipes. Upon reaching the condenser portions 27 of the heat pipes 10, where
the temperature is slightly lower than the evaporator portions 24, the
vapor 28 condenses giving off thermal energy. That thermal energy is
typically radially conducted, or to the extent such thermal energy is
transferred through the air, thermally radiated, to the outer surface 38
of the cylinder wall 30, because the outer cylinder surface is adjacent
the heat pipes 10. The uniformity achieved across the entire outer surface
38 of the cylinder wall 30 depends on the frequency of location of heat
pipes 10 around the periphery of the cylinder wall and the length of the
heat pipes relative to the length of the cylinder wall.
As mentioned above, it is important that the thermal energy imparted to the
outer cylinder surface 38 is uniform, because it is the outer cylinder
surface that comes in contact with a work piece (not shown). To uniformly
dry, heat or roll a work piece, the temperature of the heat transfer
cylinder doing the drying, heating or rolling must itself be uniform. The
invention provides such temperature uniformity to the outer surface 38 of
cylinder wall 30 of heat transfer cylinder 12.
To complete the cycle of thermal energy transfer within the heat pipes 10,
the working fluid/condensate 20 is reabsorbed into the capillary structure
22 within the heat pipe 10. In effect, the above described cycle
repeatedly updates and evenly distributes the thermal energy along the
individual heat pipes 10 in an extremely efficient and fast manner. This
is very important in maintaining a uniform temperature on outer cylinder
surface 38. For example, when localized heat from friction is imparted to
the outer cylinder surface 38 from repeated contact with a metal ingot,
such localized heat is quickly distributed throughout the heat pipes 10,
and hence throughout the entire cylinder surface. Thus, the temperature on
cylinder surface 38 stays uniform, and the thermal expansion along the
outer cylinder surface stays uniform, so that the resulting metal sheet is
of uniform thickness.
In accordance with another aspect of the invention, the heat pipes 10 are
bent slightly outwardly at 78 so that the diameter formed by the
evaporator portions 24 of the heat pipes is slightly larger than the
diameter formed by the condenser portions 27 of the heat pipes. This
aspect of the invention enhances the transfer of thermal energy in the
individual heat pipes 10 as the heat transfer cylinder 12 is rotated at
high rpm's, thereby improving the efficiency of the cylinder.
Heat pipes are particularly suited to the transfer of heat across a
cylindrical rolling or drying surface. This is due to the high efficiency
of heat pipes in providing thermal energy transport and the heat pipe's
ability to quickly dissipate localized concentrations of heat. The
efficiency of heat pipes is partly due to the fact that velocity of the
vapor within the individual heat pipes is very fast. Also, the heat
transfer process described above is driven by a very minimal temperature
gradient between the evaporator portions and the condenser portions of the
heat pipes. Indeed, it is a well known characteristic that the transfer of
large quantities of energy in heat pipes, being an isothermal transfer
process, can be accomplished at a wide range of temperatures, both high
and low. Furthermore, heat pipes 10 can easily be made to the precise
length of the outer cylinder surface 38 contacting the work piece so that
heat is evenly distributed longitudinally the length of the surface.
Likewise, the size and number of heat pipes can be varied so that
circumferential uniformity is achieved and maintained constant.
Temperature uniformity of outer cylinder surface 38 is further enhanced by
the way the invention applies heat to the heat pipes 10 of cylinder 12.
Accordingly, steam input lines 68 simultaneously apply the same
temperature heat source directly to all the evaporator portions 24 of the
heat pipes 10, so that there is virtually no temperature loss or
difference between the individual heat pipes to start with. To continue
this uniform beginning temperature among the evaporator portions 24 of the
heat pipes 10, it is a well known characteristic of heat pipes to conduct
thermal energy along the length of the heat pipes with a minimum of
temperature drop from the evaporator portions of the heat pipes to the
condenser portions. Hence, the temperature uniformity of the outer
cylinder surface 38 is further enhanced by the very characteristics of the
heat pipes 10 disposed within cylinder 12.
The heat transfer cylinder 12 of the present invention addresses the
problems left unsolved by prior art cylinders.
For example, the use of a plurality of heat pipes 10 around the periphery
of the cylinder wall 30 helps to eliminate condensate on the cylinder
wall's inner surface 36, thus also helping to eliminate the problem of
nonuniform heating attributed to varying depths of condensate on the
cylinder wall's inner surface. Likewise, the heat transfer cylinder 12 of
the present invention is more efficient, because there is no longer the
need for extra heating of the cylinder in an attempt to compensate for
nonuniform temperatures due to varying depths of condensate inside the
cylinder.
Furthermore, the need for pressure vessel construction of the heat transfer
cylinder 12 of the present invention is not necessary, because only the
heat pipes 10 contain pressurized vapor 28, not the cylinder itself. This,
of course, reduces the expense of producing such cylinders 12 because less
material is needed and stringent pressure vessel codes do not apply. Since
the cylinder wall 30 itself is not subject to vapor pressure, maintenance
is easier and less frequent, and operation of the heat transfer cylinder
12 is safer than prior art cylinders.
Referring now to FIGS. 9-13, a heat transfer cylinder 80, in accordance
with a second embodiment of the invention, is likewise suitable for
drying, rolling or otherwise processing a work piece. Like its first
embodiment counterpart, heat transfer cylinder 80 comprises a cylinder
wall 82 with first and second ends 84, 86 and inner and outer surfaces 88,
90, and end wall 92 enclosing the first end 84 of the cylinder wall 82. A
steam chest hub 94 is rigidly joined to the first end 84 of the cylinder
wall 82, and a closed hub 96 is rigidly joined to the second end 86 of the
cylinder wall.
The steam chest hub 94 of the second embodiment is virtually identical to
the steam chest hub 42 of the first embodiment, serves substantially the
same purposes, and interconnects the cylinder wall 82 with a drive shaft
98 containing an inner concentric shaft 99.
Heat transfer cylinder 80 also comprises steam input lines 100
communicating with hollow drive shaft 98, and condensate removal tubes 102
communicating with hollow inner concentric shaft 99. Steam input lines 100
and condensate removal tubes 102 function basically in the same way and
are positioned similar to their corresponding components in the first
embodiment of the invention. However, the steam input lines 100 of
cylinder 80 are slightly longer and positioned differently than their
first embodiment counterparts to allow direct spraying of steam onto the
first end 84 of the cylinder wall 82.
The heat transfer cylinder 80 of the second embodiment also comprises a
closed hub 96. Unlike the corresponding open hub 43 of the first
embodiment, this closed hub 96 does not have holes in it because it must
enclose and seal the hollow cylinder formed by the cylinder wall 82 and
the end wall 92. As with the open hub 43 of the first embodiment, the
closed hub 96 rigidly interconnects the cylinder wall 82 to another shaft
104. Thus, just like the heat transfer cylinder 12 of the first embodiment
of the invention, heat transfer cylinder 80 is driven by a drive shaft 98
and can rotate about its axis on the drive shaft and shaft 104.
As can be seen by those skilled in the art, the methods of heating and
rotating this second embodiment of the invention are nearly identical to
those in the first embodiment of the invention. As described in connection
with the first embodiment of the invention, other methods of heating and
rotating the heat transfer cylinder 80 of the second embodiment of the
invention will be apparent to those skilled in the art. Also, as will be
appreciated by those skilled in the art, a single drive shaft (not shown)
may be used to rotate the second embodiment of the invention about two or
more hubs. Like its first embodiment counterpart, 10 the second embodiment
of the invention is also suitably heated by other well known heat sources
such as electrical slip ring/brush combination, direct fire oxidation and
others.
Inasmuch as thermal energy is applied to the first end 84 of the cylinder
wall 82, the first end of the cylinder wall becomes the evaporator portion
106, leaving the rest of the cylinder, defined by the cylinder wall and
closed hub 96, to be the condenser portion 108 of the invention. Though
applying heat to the end of the cylinder wall is preferred, those skilled
in the art will see that the heat source may be directed, with varying
degrees of efficiency, at any portion of the cylinder wall 82.
Unlike the first embodiment of the invention, where individual heat pipes
10 contain the capillary structure 22 and the working fluid/condensate 20,
the second embodiment uses a capillary structure 110 (e.g., grooves,
wires, wicking material or other material serving a capillary function)
which is fixed adjacent the inner surface 88 of the cylinder wall 82.
Likewise, unlike its first embodiment counterpart, heat transfer cylinder
80 is adapted to receive and contain working fluid/condensate 112 within
the cylinder wall 82 itself, not within individual heat pipes inside the
cylinder wall.
During operation of heat transfer cylinder 80, heat is applied to the
evaporator portion 106 of the rotating cylinder in much the same way as
heat is applied to evaporator portions 24 of the heat pipes 10 of the
first embodiment. This causes the working fluid/condensate 112, being
sealed inside the cylinder wall 82, end wall 92 and closed hub 96, to
vaporize and fill the above described cylinder. After leaving the
evaporator portion 106 of the cylinder 80, the vapor gradually cools and
condenses giving off thermal energy which is transferred by conduction to
the outer surface 90 of the cylinder. The working fluid/condensate 112 is
then reabsorbed into the capillary structure 110 etched or otherwise fixed
on or adjacent the 15 inner surface 88 of the heat transfer cylinder 80.
Once the working fluid/condensate 112 is reabsorbed into the capillary
structure 110, it is brought back towards the evaporator portion 106 of
the cylinder through capillary and/or centrifugal forces.
In accordance with another aspect of the second embodiment of the
invention, the evaporator portion 106 of the cylinder wall 82 is flared
outwardly so that the diameter of the evaporator portion of the cylinder
wall is slightly larger than the diameter of the rest of the cylinder
wall. In this manner, additional acceleration forces exist during rotation
of the cylinder. These forces, in addition to otherwise existing
centrifugal and/or capillary forces, move working fluid/condensate 112 in
capillary structure 110 more rapidly away from the condenser portion 108
of the cylinder 80 and towards the evaporator portion 106 of the cylinder.
This enhances the transfer of thermal energy across the cylinder's
surfaces 88, 90.
When used as a dryer cylinder in the pulp and paper industry, the heat
transfer cylinder 80 typically may be rotated in excess of 300 rpm's. At
these high rpm's, heat transfer and temperature uniformity across outer
surface 90 are enhanced by virtue of the increased acceleration forces due
to high rotational velocity and the enlarged diameter of the evaporator
portion 106 of the cylinder 80. In other words, the higher the rotational
velocities of the heat transfer cylinder 80, the more efficient the
transfer of thermal energy across the cylinder's outer surface 90. This
increase in thermal energy transfer efficiency provides for more uniform
and constant heating of the cylinder surface and a more uniform final
product.
Furthermore, the flared design of the evaporator portion 106 of the second
embodiment, used in conjunction with the inner capillary structure 110
regulating the working fluid/condensate 112 depth on the inner surface 88
of the cylinder wall 82, greatly enhances the efficiency of the present
invention over prior art cylinders. These same considerations prevail for
the first embodiment of the invention, wherein the acceleration forces
within individual heat pipes 10 are increased due to high rotational
velocities and bending of the heat pipes outward at 78 as described above.
The particular applicability of heat pipe principles to a cylinder, as
demonstrated in the second embodiment of the invention, is apparent.
Because of the high degree of conductance and heat dissipation achievable
with a heat pipe design, more constant and uniform heating is available
with heat transfer cylinder 80 than prior art cylinders. Indeed, the
various characteristics showing the applicability of heat pipes 10 to the
heat transfer cylinder 12 described above, also suggest the applicability
of the heat pipe principle in general to cylinders used to dry, roll or
otherwise process a work piece. The advantageous properties of high speed
vapor travel and isothermal energy transfer characteristic in heat pipes,
exist in the second embodiment of the invention as well, and render the
second embodiment of the invention more efficient and uniformly heated
than prior art cylinders.
Accordingly, heat transfer cylinder 80 of the second 10 embodiment of the
present invention addresses many of the problems left unsolved by prior
art cylinders. For example, the addition of a capillary structure 110 into
the cylinder 80, especially when the cylinder rotates at high speeds,
serves to control the working fluid/condensate 112 on the inner surface 88
of the cylinder wall 82. Likewise, unlike conventional steam cylinder
dryers and rollers, only a relatively small predetermined amount of liquid
(i.e., working fluid/condensate 112) is present inside the heat transfer
cylinder 80. This is due to the fact that the cylinder 80 is sealed after
the working fluid/condensate 112 is introduced, and the heat source is
externally applied to the evaporator portion 106 of the cylinder wall 82.
To the contrary, conventional steam cylinder dryers spray steam directly
into a cylinder, and the condensate pools at the bottom of the cylinder
and exists at varying depths on the inner cylinder surface. Likewise, as
described in detail above, the flaring of the evaporator portion 108 of
the cylinder 80 improves energy transfer across the cylinder wall's outer
surface 90, which lends to the superior performance of the second
embodiment of the heat transfer cylinder 80 over prior art cylinders.
Finally, just like the first embodiment of the invention, the second
embodiment of the invention can be advantageously used in several
industries including: the pulp and paper industry, various metal rolling
industries, the food processing industry, the plastics industry, copy
machines, laminating machines, and other applications. Applied in such
areas of commerce, the second embodiment of the invention will greatly
enhance efficiency, quality of products and profitability.
While preferred embodiments of the present invention have been shown and
described, it will be apparent to those skilled in the art that many
changes and modifications may be made without departing from the invention
in its broader aspects. The appended claims are therefore intended to
cover all such changes and modifications as followed in the true spirit
and scope of the invention.
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